JPH037581Y2 - - Google Patents

Description

[Detailed description of the invention] [Industrial application field] The present invention is a swash plate type compressor that is arranged to obtain compression action by reciprocating a double-headed piston through the rocking rotation of the swash plate. In , an improvement for supplying lubricating oil to the mooring part of the shoe interposed between the swash plate and the double-ended piston,
In particular, the present invention relates to an improvement for increasing the lubrication effect on the sliding contact portion between the swash plate and the shoe.

[Conventional technology]

Generally, in a swash plate type compressor, a pair of front and rear cylinder bores are bored at regular intervals parallel to the rotation axis, with a swash plate chamber in between. In the swash plate chamber, a swash plate is mounted on the rotating shaft so as to be able to swing and rotate, while a double-headed piston is inserted into each pair of front and rear cylinder bores, penetrating the swash plate chamber so as to be able to move forward and backward. . Furthermore, a shoe is moored between the piston and the swash plate, and is provided so that the piston can be reciprocated through the rocking rotation of the swash plate. Both FIGS. 7 and 8 are drawings showing the specific structure thereof, and a spherical receiving portion is recessed on the piston side facing the swash plate chamber, and the spherical receiving portion has a spherical portion 8A. The spherical surface part 8A of the shoe 8 which has a flat part 8B and is formed into a hemispherical shape is engaged with the shoe 8, while the flat part 8B of the shoe 8 is engaged with the swash plate 6 side.
A sliding surface 19 is formed having a width S' wider than that of the sliding surface 19, and the flat portion 8B of the shoe 8 is formed with respect to the sliding surface 19.
are provided so as to be in close contact with each other over the entire surface.

[Problem that the invention attempts to solve]

However, in the case of a swash plate compressor with the conventional structure as described above, in the mooring part of the shoe, especially in the mooring part on the swash plate side, the flat part of the shoe and the sliding surface of the shoe formed on the swash plate side The problem is that sufficient lubrication cannot be obtained on the sliding surfaces. That is, in a swash plate compressor, the method of lubricating the mooring part between the swash plate and the piston is to use refrigerant gas (suction gas) that is normally sent from the evaporator to the swash plate chamber via the suction pipe.
A method of lubrication through
In this conventional lubrication method, as mentioned above, the flat part of the shoe is provided in close contact with the sliding surface formed on the slope of the swash plate over the entire surface. The refrigerant gas (suction gas) sent into the swash plate chamber is blown outward by the rocking rotation of the swash plate, causing the swash plate (sliding surface) and shoe (flat area ) has a problem in that it is not possible to supply sufficient lubricating oil to the sliding surfaces. This kind of problem is even more noticeable in cylinder bores that are far away from the opening of the suction pipe, but in this way, the relationship between the swash plate (sliding surface) and shoe (flat part) in each cylinder bore can be seen. The problem is that the sliding contact surface seizes or uneven wear occurs due to insufficient lubricating oil being supplied to the sliding contact surface, and the problem that the piston stroke becomes erroneous due to the uneven wear.
In other words, there is a backlash between the shoe and the piston, and the backlash causes noise.

The present invention is an attempt to improve the problem in order to solve the above-mentioned problems.The present invention is an attempt to improve the above-mentioned problems. The problem to be solved is to be able to supply lubricating oil smoothly to the contact surfaces, especially to be able to supply lubricating oil approximately evenly to each cylinder bore. have In other words, the present invention is based on the fact that almost no load is applied to the suction stroke side of the piston at the mooring part between the swash plate and the piston. In view of the fact that this does not play a very important role in transmitting reciprocating motion to the body, an attempt was made to improve it, and its specific means and effects are as follows.

[Means for solving problems]

The sliding surface formed on the slope of the swash plate has a flat part and a spherical part, and the flat part of the shoe, which is formed into a substantially hemispherical shape, is brought into sliding contact with the sliding surface, while the above-mentioned one is attached to the side of each double-headed piston that is inserted into each cylinder bore. In a swash plate compressor, a spherical receiving part is recessed to face the sliding surface, and the spherical part of the shoe is engaged with the spherical receiving part, and the sliding surface corresponds to the suction stroke of the piston. A cutout groove is cut across the rotation range, and the cutout groove forms a bottleneck in a part of the sliding surface. The attrition shall be formed to have the same width as the flat part of the shoe or narrower than the flat part; A state in which a part of the flat part protrudes from the bottleneck and makes sliding contact is obtained.

[Effect]

The refrigerant gas filling the swash plate chamber through the rocking rotation of the swash plate is drawn into the notch groove and rotates together with the swash plate, i.e., the rotation corresponding to the suction stroke of the piston in each cylinder bore. In this region, the sliding surface formed between the sliding surface (bottleway) of the swash plate and the flat part of the shoe can be lubricated.

〔Example〕

Hereinafter, specific embodiments of the present invention will be described with reference to the illustrative drawings.

1 to 3 are drawings showing a first embodiment, and in each drawing, 1 indicates a cylinder block. The cylinder block 1 consists of a front cylinder block 1F and a rear cylinder block 1R, both cylinder blocks 1F and 1R.
A shaft hole 2' is provided in the center of the shaft,
The rotating shaft 2 is rotatably supported in the coaxial hole 2' via bearing parts 16, 16. And the same rotation axis 2
One end passes through a front housing 15F (described later) and is connected to an electromagnetic clutch (not shown), which transmits the driving force of the engine (not shown) to the rotating shaft 2 through connection and disconnection of the electromagnetic clutch. It is set up so that it can be done. Further, an appropriate number (5) of cylinder bores 3 are provided on the outer periphery of the axial hole 2' in parallel with the coaxial hole 2'. That is, they are arranged at regular intervals on the same circumference so as to surround the shaft hole 2'.

Each cylinder bore 3 is divided into a front side and a rear side so as to form a front and rear pair with a swash plate chamber 4 in between.
A compression chamber 7 exists between valve plates 10F and 10R, which will be described later, and a double-headed piston 5 is fitted therein so as to be able to move forward and backward. Further, in the swash plate chamber 4, a swash plate 6 is mounted on the rotating shaft 2 so as to be swingable and rotatable. A shoe 8 is moored between the slope (sliding surface 19) of the swash plate 6 and the piston 5.
It is provided so that the swinging rotation of the piston 5 can be transmitted to each piston 5 as a reciprocating motion. More specifically, the double-headed piston 5 is provided with a pair of front and rear piston heads 5A, 5A facing each other with a mooring space 5B in between, and both piston heads 5A, 5A are fitted into the cylinder bore 3 so as to be freely retractable. Both piston heads 5A, 5A are the same piston head 5A,
It is formed by integrally connecting the bridge 5C with a curved bridge 5C having the same arc as the outer peripheral surface of the bridge 5A. Spherical receiving parts 9, 9 are recessed on the rear surfaces of both piston heads 5A, 5A to face the mooring space 5B, and the spherical receiving parts 9, 9 have a spherical part 8A and a flat part 8B. Hemispherical (dome-shaped)
The spherical surface portion 8A of the shoe 8 formed in the above-mentioned shoe 8 is provided so as to be rotatably engaged in the universal direction.

On the other hand, each double-ended piston 5 is provided on the slope of the swash plate 6.
A sliding surface 19 of the shoe 8 is formed in an endless shape so as to face the shoe 8, and is provided so that the flat portion 8B of the shoe 8 can be brought into sliding contact with the sliding surface 19. The sliding surface 19 has a bottleneck 19 in a part thereof.
A is formed. The same bottleneck 19A corresponds to the rotation range of each double-headed piston 5 during its suction stroke (range of 140° to 330° on the coordinate axes shown in FIG. 3).
It is formed by cutting a plurality of notch grooves 19B, 19B extending in the rotational direction. More specifically, the bottleneck 19A is formed to have a width S that is the same as the diameter R of the flat portion 8B of the shoe 8 or smaller than the diameter R of the flat portion 8B. When the width dimension S of the same bottleneck 19A is smaller than the diameter dimension R of the flat part 8B, the first
As shown in each drawing of FIG. 3, a part of the flat part 8B is provided so as to be able to slide in a state protruding from both left and right edges of the bottleneck 19A.

Further, 15F is a front housing that covers the open end of the front cylinder block 1F with the front valve plate 10F in between, and 15R is a rear housing that also covers the open end of the rear cylinder block 1R with the rear valve plate 10R in between. and both housings 15F, 15
In R, suction chambers 17F, 17R and discharge chambers 18F, 18R are provided concentrically in correspondence with each cylinder bore 3 with an annular partition between them. That is, the discharge chambers 18F and 18R are located in the center, and the suction chambers 17F and 17R are located in the same discharge chamber 18.
It is located near the periphery so as to surround F and 18R. And front valve plate 10F
And the above-mentioned suction chamber 1 is installed on the rear valve plate 10R.
Suction ports 11F and 11R correspond to 7F and 17R.
However, discharge ports 12F and 12R are opened correspondingly to the discharge chambers 18F and 18R, respectively. Further, suction valves 13F and 13R are provided at the suction ports 11F and 11R so as to be located on the compression chamber 7 side so as to be able to open and close freely through the suction stroke of the piston 5, and the discharge port 12
Discharge valves 14F and 14R are provided in F and 12R so as to be located on the side of the discharge chambers 18F and 18R and can be opened and closed via the compression stroke of the piston 5.

FIG. 4 is a drawing showing the second embodiment,
Notch grooves 19B carved on both sides of the bottleneck 19A,
19B is formed by arranging a large number of notched grooves 19B', 19B' in a line at regular intervals along the rotation direction.

In both of the above embodiments, a plurality of cutout grooves 19B are provided along both sides of the bottleneck 19A, but the cutout grooves do not necessarily need to be provided on both sides of the bottleneck 19A. Instead, it is also possible to provide it only on one of them.

Next, its effect will be explained.

In the first embodiment shown in FIGS. 1 to 3, the swash plate 6 is oscillated in the swash plate chamber 4 by transmitting the driving force of the engine to the rotating shaft 2 through the connection operation of an electromagnetic clutch (not shown). A state of dynamic rotation is obtained. Since a shoe 8 is anchored to the peripheral edge of the swash plate 6 between it and the piston 5, the swinging rotation of the swash plate 6 is transmitted to each piston 5 via the shoe 8, and each piston 5 A state of continuous reciprocating movement within the cylinder bore 3 is obtained.

On the other hand, a suction pipe 20 is connected from the evaporator to the compressor.
The refrigerant gas that has been pumped inside is sent into the swash plate chamber 4, and a state is obtained in which the swash plate chamber 4 is filled with the refrigerant gas. Suction chamber 17F, 1
Sent into 7R. The refrigerant gas sent into the suction chambers 17F, 17R in this manner is transferred to the suction valves 13F, 13R via the negative pressure generated in the cylinder bore 3 during the suction stroke of the piston 5.
Force open the intake ports 11F, 11F, 11R.
The refrigerant gas thus sucked into each cylinder bore 3 is compressed through the exhaust stroke of the piston 5 and is also compressed through the discharge valves 14F and 14R through the same compression action.
The effect of forcibly pushing open the gas and sending it into the discharge chambers 18F, 18R from the discharge ports 12F, 12R, that is, the compression effect is obtained.

On the other hand, since the swash plate chamber 4 is filled with refrigerant gas as described above, a part of the refrigerant gas is drawn into the notch groove 19B through the rocking rotation of the swash plate 6. A state in which the swash plate 6 rotates together with the swash plate 6 is obtained. And like this, the refrigerant gas enters the notch groove 1.
By being caught in the swash plate 9B and rotating together with the swash plate 6, the sliding surface of the swash plate 6 (bottleway 19A) and Show 8
The effect of lubricating the sliding surfaces formed between the flat portion 8B and the flat portion 8B can be obtained. In addition, a part of the refrigerant gas caught in the notch groove 19B as described above scatters in the form of a spray while rotating together with the swash plate 6, and lubricates other mooring parts, bearing parts, etc. That is,
An effect of generally enhancing the lubrication effect within the swash plate chamber 4 can be obtained.

Moreover, since the cutout groove 19B functions as a passage for the refrigerant gas, the effective passage area for the refrigerant gas in the swash plate chamber 4 can be substantially expanded accordingly.

On the other hand, in the second embodiment shown in FIG.
By arranging B' in a line at regular intervals, refrigerant gas is stored in each notch groove 19B' to ensure rotation, that is, to further enhance the lubrication effect. can get.

As a result of a comparative experiment conducted by the present applicant with a conventional structure, the results shown in FIG. 5 in terms of seizure resistance and the results shown in FIG. 6 in terms of abrasion resistance were obtained.

[Effect of idea]

The present invention is constructed as described above.
As mentioned above, on the sliding surface of the shoe formed on the slope of the swash plate, a cutout groove is carved in the part corresponding to the rotation range in the suction stroke of the piston, with a bottleneck in the sliding surface, and By oscillating the refrigerant gas filling the swash plate chamber into the notched groove and rotating it together with the swash plate, the sliding surface of the swash plate and the swash plate are connected to each other in each cylinder bore. It has now become possible to effectively supply refrigerant gas (lubricating oil) to the sliding surface formed between the flat part and the flat part. In other words, it becomes possible to supply refrigerant gas (lubricating oil) almost evenly to the sliding surface between the swash plate and the shoe formed in each cylinder bore, and as a result, the sliding surface between the swash plate and the shoe In addition to being able to prevent seizure in the piston, it has also become possible to effectively prevent uneven wear and the rattling of the piston stroke and noise caused by the uneven wear.

[Brief explanation of drawings]

1 to 3 are drawings showing the first embodiment, in which FIG. 1 is a sectional view showing the entire swash plate compressor, and FIG. 2 is an enlarged sectional view of the mooring portion between the swash plate and the shoe. FIG. 3 is an enlarged front view of the same. FIG. 4 is a drawing showing the second embodiment, and is an enlarged front view of the mooring portion between the swash plate and the shoe. Further, FIG. 5 is a graph showing a comparison of temperature rise (seizing) between the present invention and the conventional structure, and FIG. 6 is a graph showing a comparison of the amount of wear. 7 and 8 are drawings showing a conventional structure, in which FIG. 7 is an enlarged sectional view of the mooring portion between the swash plate and the shoe, and FIG. 8 is an enlarged front view thereof. 1...Cylinder block, 1F...Front cylinder block, 1R...Rear cylinder block, 2...Rotating shaft, 2'...Shaft hole, 3...Cylinder bore, 4...Swash plate chamber, 5...Double-ended piston , 5A... Piston head, 5B... Mooring space, 5C... Bridge, 6... Swash plate, 7... Compression chamber, 8... Shoe, 8A... Spherical part, 8B... Flat part, 9... Spherical receiver, 10F...Front valve plate, 10R...Rear valve plate,
11F, 11R... Intake port, 12F, 12R...
Discharge port, 13F, 13R... Suction valve, 14F, 1
4R...Discharge valve, 15F...Front housing, 15R...Rear housing, 16...Bearing section, 17F, 17R...Suction chamber, 18F, 18R
...discharge chamber, 19 ... sliding surface, 19A ... bottleneck,
19B... Notch groove, 20... Suction pipe line, 21
...A passageway.

Claims (1)

[Scope of Claim for Utility Model Registration] (1) A plurality of sets of cylinder bores are bored parallel to the rotation axis, facing each other on the front side and the rear side so as to form a pair of front and rear sides with a swash plate chamber in between. In the swash plate chamber, a swash plate is mounted on the rotating shaft so as to be able to swing and rotate freely, and the swash plate has a flat part and a spherical part on its slope, and the flat part of the shoe, which is formed into a substantially hemispherical shape, is slid. On the other hand, a double-headed piston is fitted into each cylinder bore so as to be able to reciprocate, and the double-headed piston has a pair of front and rear spherical receiving portions facing each other and recessed therein. In a swash plate type compressor in which spherical parts are engaged, a notch groove is cut in the swinging surface between the slope of the swash plate and the flat part of the shoe over a rotation range corresponding to the suction stroke of the piston. A lubrication mechanism for a shoe mooring part in a swash plate compressor, in which a cutout groove forms a bottleneck having the same width as or narrower than the flat part of the shoe. (2) The above-mentioned notched groove is formed by arranging a large number of notched grooves in a line at regular intervals. Scope of Utility Model Registration Lubrication mechanism.